FR2600296A1 - WINDSCREEN WIPER DEVICE, WITH NON-CIRCULAR WIPING - Google Patents

Abstract

THE WIPER DEVICE INCLUDES A DRIVE HEAD 5 INTENDED TO BE SUBJECT TO AN ALTERNATIVE ROTATION MOVEMENT, A WIPER ARM 6 MOUNTED ON THE HEAD SO, on the one hand, TO BE DRIVEN IN THE WIPER. GENERAL MOVEMENT OF ALTERNATIVE ROTATION OF THE HEAD, AND, ON THE OTHER HAND, TO BE ABLE TO BE MOVED IN TRANSLATION, RELATIVE TO HEAD 5, FOLLOWING THE LONGITUDINAL DIRECTION L OF THIS ARM. CONTROL MEANS ARE FURTHER PROVIDED FOR COMMUNICATING TO HEAD 5 ITS ALTERNATIVE ROTATION MOVEMENT, AND TO ARM 6 ITS TRANSLATION MOVEMENT IN RELATION TO THE HEAD, THE CONTROL MEANS OF THE ARM INCLUDING A CRANK 8 ANIMATED BY A MOVEMENT OF ROTATION AROUND THE SAME ROTATION AXIS AS THAT OF THE HEAD 5. THE CRANK 8, SPECIFIC TO MOVING THE WIPER ARM 6 IN TRANSLATION, IS ANIMATED BY AN ALTERNATIVE ROTATION MOVEMENT WITH AN AMPLITUDE LESS THAN 180 AND THE CONTOUR OF THE DRIVE HEAD 5, AT THE LEVEL OF THE CRANK, SHAPES A SENSITIVELY CIRCULAR SECTOR CORRESPONDING TO AN ANGLE B ALSO LESS THAN 180.

Description

WINDSCREEN WIPER DEVICE, WITH NON-CIRCULAR WIPING.

  The invention relates to a wiper device, with non-circular sweeping, of the type which includes a drive head intended to be subjected to an alternating rotational movement, a wiper arm mounted on the head. so as, on the one hand, to be driven in the general reciprocating rotation movement of the head, and, on the other hand, to be able to be moved in translation, relative to the head, in the longitudinal direction of this arm , control means being further provided for communicating to the head its reciprocating rotational movement, and to the arm its translational movement relative to the head,

  the control means of the arm comprising a crank driven by a rotational movement around the same axis of rotation as that of the head.

  It is known that non-circular scanning aims to establish a larger scanning surface than that obtained by circular scanning, in particular by increasing this scanning surface in the region of the corners remote from the surface to be wiped, in particular a windshield. of vehicle

  automobile. The wiper devices of the type targeted by the invention make it possible to obtain such non-circular wiping by combining a translational movement of the arm, in its longitudinal direction, with the conventional reciprocating rotational movement of this arm.

  The combination of these two movements poses production problems, in particular in terms of the size of the various mechanisms required, as well as in terms of their

  complexity and number of moving parts.

  The object of the invention is, above all, to provide a non-circular wiper device, of the type defined above, which meets better than hitherto the various requirements of practice and which, in particular, is d '' a small footprint, while ensuring good precision of movement control, while remaining

  of a relatively simple realization.

  According to the invention, a wiper device, with non-circular sweeping, of the type defined above is characterized in that the crank proper-to move in translation the wiper arm is driven by a movement of alternating rotation of an amplitude less than and that the contour of the drive head, at the level of the crank, has the shape of a substantially circular sector corresponding to an angle also less than 180. 10 Preferably, the angle between the extreme radii

  of the drive head sector is less than 900.

  The crank can be directly connected to the end of the wiper arm by a cardan type transmission joint, the wiper arm being mounted with a possibility of oscillation relative to a guide linked to the head. Such a possibility of oscillation is advantageously obtained from the fact that the wiper arm is slidably mounted in a spherical ball joint carried by the end 20 of the guide linked to the head. The arm may be in the form of a

  clean cylindrical rod to slide in a corresponding bore in the ball joint.

  Alternatively, the arm is animated with a

  rectilinear translational movement and connecting means 25 are provided between the end of the crank and the arm.

  These connecting means may comprise a connecting rod articulated at one end on the crank and, at the other end,

on the arm.

  The crank suitable for controlling the translational movements of the arm is locked in rotation on a driven shaft; born in a first reciprocating rotary motion, said shaft freely traversing in rotation a bearing for the drive head, as well as a shaft hollow, coaxial,

  intended to be driven by another native alter35 rotation movement, this hollow shaft being linked in rotation to the head

  dragging, so as to control the movement of this head. The hollow shaft may have a radial extension, for the connection in rotation with the drive head, this connection being provided by a pin / housing system, or equivalent, provided towards the end of the remote extension

  of the geometric axis of the hollow shaft.

  The crankshaft ensuring the reciprocating movements in translation of the arm is controlled by means sensitive to the angular position of the drive head relative to a frame, fixed relative to the surface

to wipe.

  Advantageously, the means for controlling the crankshaft comprise a support driven in the reciprocating rotational movement of the drive head, this support being provided in an area radially distant from the geometric axis of the drive shaft. the crank, of a rotary member, in particular a pinion, mounted to rotate freely relative to the support but linked in translation to this support, this rotary member being able to roll, without sliding, against the internal surface of a track, in a circular crown arc, fixed relative to the above-mentioned structure, a connecting rod,

  or equivalent, being provided between an eccentric point of the rotary member and a radial extension linked in rotation to the shaft of the crank.

  The support can be formed by at least one flat element, or equivalent, linked in rotation to the hollow shaft intended to control the drive head, this flat element, whose plane

  means is orthogonal to said shaft, extending radially and carrying, at its end remote from the shaft, the aforesaid rotary member.

  Preferably, the support is formed by two parallel flat elements spaced from one another in the direction of the hollow shaft, each flat element carrying, inwards, a rotary member, advantageously a pinion, while the connecting rod is located between the two

  pinions, each pinion cooperating with a circular crown provided inside a case fixed to the frame.

  The connecting rod can be articulated on the ex5 tension linked to the crankshaft.

  According to another possibility, the connecting rod is provided, at its end near said extension, with a rack capable of cooperating with a pinion, wedged

  on the crank shaft, the outer surface of this pinion constituting the extension.

  The invention consists, apart from the arrangements set out above, of a certain number of other arrangements which will be more explicitly discussed below in connection with particular embodiments described with reference to the attached drawings, but which are in no way limiting. FIG. 1, of these drawings, is a partial diagram,

  in elevation, a windshield and a non-circular wiper device.

  Figure 2 is a top view, with parts

  cut, of a wiper device according to the invention.

  Figure 3 is an elevational view, with parts

  cut, of the device of Figure 2.

  - Figure 4 is a sectional view along the line

IV-IV figure 2.

  FIG. 5 is a view, in section along V-V,

Figure 4, a detail.

  Figure 6 is a top view, similar to Figure 2, of an alternative embodiment of the device.

  FIG. 7 is a simplified diagram illustrating the relative positions of the elements of the device, for a minimum effective arm length in an extreme scanning position. Figure 8 is a diagram, similar to that of Figure 7, for a corresponding intermediate position

at maximum arm extension.

  Figure 9 is a diagram similar to that of

  Figure 7, for the position of the arm in the middle of the windshield.

  Figure 10 is a sectional view along the line

  X-X, FIG. 11 means for controlling the alternative rotational movements.

  Figure 11 is a top view, with parts

  broken away, control means of FIG. 10.

  Figure 12 shows, similarly to Figure 10,

  an alternative embodiment of the control means.

  FIG. 13, finally, is a partial top view of the means of FIG. 12.

  Referring to Figure 1 of the drawings, one can see a wiper device 1 with non-circular sweep for a windshield 2 of a motor vehicle. Generally, such a wiper device is of the monobroom type; it is however possible to provide a non-circular wiping for the wiper devices with several brushes. The outer contour of the swept surface has been represented by a line 3 in dashed lines which is situated, in the zone of the upper remote corner of the windshield shown in FIG. 1, outside of a conventional circular sweep contour

  represented by the dashed line 4, from which an increase in the swept area 25.

  The device 1 comprises a drive head 5 intended to be subjected to an alternating rotational movement, a wiper arm 6 mounted on the head 5 so as, on the one hand, to be driven in the general movement of 30 alternating rotation of the head 5, and, on the other hand, being able to be moved in translation, relative to the head 5, in the longitudinal direction (represented by a

  double arrow L in FIG. 1) of this arm. The arm 6 carries, at its end, in a conventional manner, a wiper blade 7 provided with a scraper blade.

  Control means B (Figure 4) are provided to communicate to the head 5 its reciprocating rotational movement, while control means C (see Figures

  2 to 4) are provided to communicate to the arm 6 its movement of transla5 tion relative to the head.

  The control means C of the arm comprise a crank 8 driven by "n rotational movement around the same geometric axis of rotation A (FIG. 4) as that of the

head 5.

  This crank 8, suitable for displacing in translation the arm 6 of the wiper (see FIGS. 2 and 3) is driven by an alternating rotational movement of an amplitude d (see FIG. 2) less than 180, and the contour 9 ( see Figure 2) of the drive head 5, at the crank 8, has the shape of a substantially circular sector corresponding to an angle 'also less than 180. In practice, the angles o and t are equal or substantially equal.

  Preferably, the angles a and p are less than 20,900.

  The amplitude H (FIG. 2) of the reciprocating translational movement corresponds to the movement, in the direction L, of the end part of the crank 8, distant from the axis

  geometric A of rotation, linked to the arm 6. This amplitude H 25 can be of the order of 80 mm.

  According to the embodiment of FIGS. 2 to 4, the crank 8 is directly linked to the associated end of the arm 6

  windscreen wiper by a transmission joint 10 of the cardan type, the wiper arm 6 being mounted with a possibility 30 of oscillation relative to a guide 11 linked to the head 5.

  More precisely, the head 5 can be formed by a sort of bowl (see FIG. 3) open upwards, and limited by a side wall 12 forming a rim which extends along the contour 9 of the head. A passage 13 (see FIG. 2) 35 is provided in the wall 12 towards one of the ends of a part 14 formed by a portion of a cylinder, --------- and a flat wall 15, - - ------------------- delimiting a straight edge of the sector. The ends of the part 14 and of the wall 15 are shaped according to parts 16 and 17, paral5 lèles, delimiting the passage 13. These parts 16 and 17 may include an extension (see FIG. 3) at their end remote from the bottom of the bowl formed by the head. The extensions of these parts 16 and 17 serve as an articulation bearing to an axis 18 orthogonal to the mean direction of the arm 6, axis on which the guide 11 is articulated. The width g of the passage 13 is sufficient to allow slight transverse deflections.

  from the end of the arm 6 linked to the end of the crank 8.

  The guide 11 is formed by a sort of envelope, substantially frustoconical, the diameter of which decreases progressively as one moves away from the head 5. The end 19 of this guide 11 is cylindrical and carries a spherical ball joint 20, in particular in material ------- self-lubricating. The ball joint 20 has a cylindrical bore 21 in which slides with gentle friction

  the arm 6 formed by a cylindrical rod.

  The seat 22 of the ball joint is fixed in the end 19 of the guide 11. The guide 11 is open in the zone 23 (FIG. 3) located on the side of the arm 6 opposite the axis 18. A tension spring 24 is tensioned between a transverse pin 25 carried 25 by the guide 11 and a hooking hole 26 provided in the head 5. The spring 24 is intended to apply the arm 6 and the

  brush 7 with sufficient pressure against the surface to be wiped. A cover D is provided for closing the head 5.

  The end of the crank 8 is provided with a yoke 30 27 whose branches are inclined, relative to the direction

  middle of crank 8, towards passage 13.

  The other end 28 of the crank 8 is locked in rotation on a shaft 29 (Figure 4) driven in a first reciprocating rotational movement. The crank 8 is generally constituted by a tubular element and the end 28 has a bore 30 (FIG. 5), of axis orthogonal to that of the crank. This bore 30 is intended to be crossed by the end 31 (FIG. 4) of smaller diameter, 5 of the shaft 29. Said end 31 comprises, at the end, a thread making it possible to screw a nut 32 intended for blocking the crank 8 on the shaft 29. A fluted frustoconical shoulder 33 constitutes the transition between the part with the largest diameter of the shaft 29 and the end 31 with the smallest diameter. A sleeve 34 is threaded around the end 31

  and extends axially beyond the shoulder 33.

  This marnchon 34 has a head 35 (FIG. 5) of larger diameter so that a shoulder 36 is formed at the junction of this head and the rest of the sleeve 34. This sleeve 15 34 has an internal bore 37 whose diameter is equal to that of the shaft 29, this bore opening into another bore 38 of larger diameter, an internal shoulder 39 ensuring the transition between these two bores. The head 35

  comprises a bore, of axis orthogonal to that of the sleeve 34, 20 intended to be crossed by the end 28 of the crank 8.

  A spacer 40, provided with a frustoconical internal housing, comprising grooves conjugated with those of the part 33 is provided to be received in the bore 38, between the part 28 of the crank and the shoulder 39. Another between 25 height rod 41 is provided to be housed in said bore

  38, against the end portion 28 of the crank, on the side opposite to the spacer 40.

  The tightening of the nut 32 which acts, by means of a washer 42 (FIG. 4) on the stack of the spacers 30 40, 41 and of the end part 28, makes it possible to apply the

  frustoconical housing of the spacer 40 on the part 33, and of locking the crank 8 in rotation relative to the shaft 29.

  The sleeve 34, by its part of smaller diameter than the head 35, freely rotates through a bearing 43. 35 The axial stop of the sleeve 34 relative to the bearing 43 is ensured, on the one hand, by the shoulder 36 and, on the other hand, by an elastic ring 44 (FIG. 4) anchored in a groove 45 provided on the external surface of the end of the sleeve 34 remote from the head 35. Because the sleeve 34 is linked in rotation to the shaft 29, it can be said that the freedom in rotation of the sleeve 34 relative to the bearing 43 means that the shaft 29 freely traverses this bearing 43 in rotation. The cup forming the drive head 5 comprises a sleeve 46 in which the bearing 43 is blocked, in particular by force fitting. Thus, the guiding in rotation of the

  drive head 5, around the geometric axis A is provided by the cooperation of the bearing 43 and the sleeve 34.

  The shaft 29, which is held by means not shown so as to be able to rotate about its geometrical axis A, 15 passes freely in rotation through a hollow shaft 47 situated above the head 5, on the side opposite to the crank 8. This tree 47 can

  turn in a fixed sleeve 48 integral with the frame. The hollow shaft 47 is intended to be driven by an alternating rotational movement different from that of the shaft 29. This hollow shaft 47 is linked in rotation to the drive head 5 so as to control the movement of this head.

  This rotational connection is ensured, in the example shown, by a radial extension 49 (FIG. 4) integral in rotation with the end of the hollow shaft 47, said extension comprising at its end remote from the axis A a pin 50, 25 provided with a rotary roller 50a, suitable for entering a housing 51 provided on

  on the bottom of the head 5, on the side opposite the crank 8.

  It is immediately understood that by communicating to the shaft 29 and to the hollow shaft 47 the appropriate alternative rotational movements, it will be possible to obtain: - an overall rotational movement, created by the hollow shaft 47 which drives the head 5, - a reciprocating translational movement of the arm 6, in its longitudinal direction L, resulting from the reciprocating rotational movement of the crank 8 caused by the shaft 29. 35 The solution of FIGS. 2 to 4 involves only a minimum of parts, for a reduced overall size of the head 5.The arm 6, in addition to its translational movement, is animated by a slight oscillating movement between extreme positions represented by mixed lines-forming an angle ( in FIG. 2, which is made possible by the ball joint 20. The value of the angle Y is reduced and this oscillation is not troublesome, however, if it is desired that the arm 6 is animated by u- rectilinear translational movement, provision may be made, 10 depending on the variant of the figur e 6, connecting means 52 between the end of the crank 8 and the arm 6. These connecting means 52 are advantageously formed by a connecting rod 53 articulated, at one end, on the crank 8, using a transmission joint 54 of the universal joint type, and, at its other end, on the arm 6 by another transmission joint 55 also of the universal joint type. The arm 6 is guided in rectilinear translation by a cylindrical sleeve 56 held by the

guide 11.

  The hollow shaft 47 is set in reciprocating rotational movement with respect to the fixed frame, to which the sleeve 48 is linked, by any suitable conventional system, in particular a system with connecting rod-crank or articulated deformable quadrilateral, of the

  genre Tchebycheff cross as described, for example, in patent application FR n 85 00069 filed January 4, 1985 25 in the name of the Applicant Company.

  The input of this reciprocating rotational movement on

  the hollow shaft 47 can be secured using a crank such as 57 (FIG. 10) locked in rotation on an extension 58, situated on the side opposite to the extension 49, this extension 58 being linked in rotation to the hollow shaft 47.

  The crank shaft 29 is controlled by

  means K sensitive to the angular position of the drive head 5 relative to the frame ---------- ixe relative to the surface to be wiped 2 (Figure 1).

  The means K comprise, as visible in the FIGS. 10 and 11, a support 59 driven in the reciprocating rotational movement of the head 5. This support 59 is provided, in an area radially distant from the geometric axis A of the shaft 29, of at least one rotary member M, in particular a pinion 60 mounted free in rotation relative to the support 59, but linked in

  translation to this support. In practice, the pinion 60 is rotatably mounted on an axis 61 carried by the support 59.

  The rotary member M is able to roll, without sliding, against the interior surface of a track 62 in an arc of a circular crown 10 fixed relative to the above-mentioned structure. Generally, this track 62 is formed by a circular sector comprising teeth suitable for meshing with those of the pinion 60. The track 62 is advantageously provided on the internal cylindrical surface of a housing 63 (FIG. 10) or equivalent fixed on the frame. A connecting rod 64 is provided between an outermost point of the pinion 60 and a radial extension 66 which is linked

  in rotation to the shaft 29 of the crank.

  The point 65 can be formed by a lug carried by one face of the pinion 60 and situated at a radial distance e (FIG. 11) from the center of the pinion 60. The connection of the other

  end of the connecting rod 64 and the extension 66 is also provided by a hinge.

  The support 59, according to the embodiment of FIGS. 10 and 11, is formed by two flat elements 67, 68, parallel, the plane of which is orthogonal to the axis of the shaft 29. The flat elements 67-, 68 are separated one from the other in the direction of the hollow shaft 47 and the geometric axis A. These two elements 67, 68 are made integral with each other by any appropriate means, the element 67 being crossed by the hollow shaft 47 to which it is linked in rotation, in particular by a pin 69, while the flat element 68 is made integral with the extension 58 for example also by a pin 70. Each flat element 67, 68 carries, towards inside, a pinion such as 60 while the connecting rod 64 is located between the two pinions. Each pinion 60 cooperates with a corresponding circular crown 62 provided inside the case 63. This case can be made in two parts

  can be separated from each other.

  The operation of the scanning device, in accordance with the invention, equipped with the control means K will be described briefly with reference to Figures 7 to 9 which schematically represent the elements or parts already described and designated by the same references

  numeric or by the same letters without their description

be taken up in detail.

  The position of the head 5 in FIG. 7 corresponds to the extreme angular position of the arm 6 in the counterclockwise direction when looking at FIG. 7 (or FIG. 1). The extension 49, as well as the head 5 occupy their extreme angular position in the

anticlockwise.

  The crank 8 occupies, relative to the head 5, its extreme angular position in the clockwise direction. The arm 6 is retracted to the maximum which corresponds to an effective length

of arm 6 minimum.

  The sweeping movement continues, from the position of FIG. 7, by a rotation movement of the head 5 clockwise. The support 59 linked in rotation to this head 5, also moves clockwise, driving the axis 61 of the pinion 60, which rolls against the track 62 fixed relative to the frame. The pinion 60 will therefore rotate, about its axis 61, counterclockwise so that the articulation point 65 of the connecting rod 64, which was as far as possible from the axis A in the position of the figure 7., will approach this axis A. When the pinion 60 has rotated approximately 1800 around its axis 61, from the position in FIG. 7, point 65 will be brought as close as possible to axis A as shown in Figure 8. The crank 8 will then occupy, 'relative to the head 5, its extreme angular position in the counterclockwise direction. This position corresponds to the maximum extension 35 of the arm 6 and therefore to the maximum effective length of this arm. The radii of the pinion 60 and the track 62 are chosen so that this extension occurs for an angular position of the head 5 corresponding to an angle

  remote: upper side of windshield 2 as already explained above.

  The head 5 continues its movement clockwise. The pinion 60 continues to rotate anti-clockwise relative to its axis 61. The articulation point 65 moves away from the axis A and causes the extension 66 and the 8 worm crank

  the maximum withdrawal position relative to the head 5.

  We find, in Figure 9, this position of maximum withdrawal of the arm 6 relative to the head 5, similar to that of Figure 7, the head 5 having however rotated by

compared to the fixed frame.

  The position in FIG. 9 corresponds to the position 15 of the arm 6 in the middle of the windshield 2.

  From FIG. 9, the movement of the head 5 continues in the counterclockwise direction and, once again, the articulation point 65 will approach the axis A causing the extension movement of the arm 6. This extension becomes again maximum 20 for an angular position of the arm 6 corresponding to the other upper corner of the windshield 2 (see FIG. 1) The head 5 will continue its movement until its extreme angular position, to the right with respect to FIGS. 7 to 9, corresponding to the inversion position of the movement 25 of the head 5. For this extreme position, the crank 8 and

  the arm 6 will have resumed, with respect to the head 5.1a maximum withdrawal position corresponding to that of FIGS. 7 and 9, but for an angular position of the head 5 different with respect to the frame. The head 5 starts again in the other sense and so on.

  Figures 12 and 13 illustrate an alternative embodiment of the means K controlling the shaft 29 of 11 crank.

  The elements of this variant are designated by the same

  numerical references as in Figures 10 and 11, possibly followed by the letter a. The detailed description of these elements will not be repeated.

  The essential difference between the embodiment of FIGS. 12 and 13, and that of FIGS. 10 and 11, resides in the fact that the connecting rod 64a of FIGS. 12 and 13 is provided, at its end remote from the point of articulation 65 of 5 the pinion 60, a rack 71, provided on the side of the rod 64a facing the geometric axis-A. The extension 66 of FIGS. 10 and 11 is replaced by a pinion 72 wedged on the axis 29, the external peripheral toothing of this pinion cooperating with the rack 71; the external surface of this pinion constitutes, in a way, a means equivalent to extension 66 and to its articulation. A yoke 73 rotatably mounted on

  the axis 29 is provided to maintain the rack 71 in mesh with the pinion 72.

  The operation of the control means K of FIGS. 12 and 13 is similar to that which has been described previously with reference to FIGS. 7 to 9.

  Whatever the embodiment adopted, the non-circular scanning device according to the invention

  is of reduced size, in particular at the level of the drive head 5, and comprises a minimum number of parts.

  The operation of this device is reliable and its construction relatively robust and economical.

  Another advantage of this device consists in replacing the brush holder; it suffices to loosen and remove the fixing nut 32 after having removed a protective cover to remove the brush holder assembly and replace it with a new assembly centering on a roller pin forming part of the transmission system movement mounted on the body. This assembly does not have to be replaced often, because the wearing part is the wiper blade and this is conventionally mounted on the wiper blade for easy replacement.

Claims (11)

  1.Wiper device, with non-circular sweep, comprising a drive head (5) intended to be subjected to an alternating rotational movement, a wiper arm (6) mounted on the head (5 ) so as, on the one hand, to be entrained in the general reciprocating movement of the head, and, on the other hand, to be able to be moved in translation, relative to the head, in the longitudinal direction (L) of this arm, control means (B, C) being further provided for communicating to the head (5) its reciprocating rotational movement, and to the arm (6) its translational movement relative to the head (5), the control means (C) of the arm comprising a crank (8) driven in a rotational movement around the same axis of rotation (A) as that of the head (5), characterized in that the crank (8) suitable for moving in translation the wiper arm (6) is driven by an alternating rotational movement of an amplitude less than 180 and that the contour (9) of the drive head (5), at the crank, has the shape of a sector substantially   circular corresponding to an angle (é) also less than 20,180.   2. Device according to claim 1 characterized   by the fact that the angle (f) between the extreme radii of the sector of the drive head (5) is less than 900.   3. Device according to claim 1 or 2 carac25 terized in that the crank (8) is directly connected to the end of the wiper arm (6) by a transmission joint (10), of the cardan type , the wiper arm (6) being mounted with a possibility of oscillation relative to a guide (11) linked to the head.   4. Device according to claim 3 characterized in that the wiper arm (6) is slidably mounted in a spherical ball joint (20) carried by the end of the guide (11) linked to the head.   5. Device according to claim 1 or 2 characters   laughed at by the fact that the arm (6) is driven in a rectilinear translational movement relative to a guide (11) linked to the head and that connecting means (52) are provided between the end of the crank ( 8) and the arm (6), the connecting means possibly comprising a connecting rod (53) articulated at one end on the crank and, at the other end on the arm (6).   6. Device according to any one of the preceding claims, characterized in that the crank 10 (8) capable of controlling the translational movement of the arm (6)   is locked in rotation on a shaft (29) driven in a first reciprocating rotational movement, said shaft (29) freely traversing in rotation a bearing (43) for the drive head (5), as well as a hollow shaft ( 47), coaxial, des15 tiné to be animated by another movement of alternative rotation,   this hollow shaft (47) being linked in rotation to the drive head (5) so as to control the movement of this head.   7. Device according to claim 6 characterized in that the hollow shaft (47) has a dia ra20 extension (49) for the connection in rotation with the drive head (5), this connection being provided by a pin system (50) / housing (51), or equivalent, provided at the end of the extension (49) remote from the geometric axis (A) of the shaft hollow (47).   8. Device according to any one of the preceding claims, characterized in that the shaft (29) of   the crank (8) ensuring the alternative movements in translation of the arm (6) is controlled by means (K) sensitive to the angular position of the drive head (5)   relative to a frame, fixed relative to the surface to be wiped.   9. Device according to ----------- claim 8 ---- characterized in that the control means (K) of the shaft (29) of the crank (8) comprise a support (59) driven in the rotatio alterna35 tif movement of the drive head (5), this support (59) being provided in an area radially distant from the geometric axis (A) of the crank shaft, d '' a rotary member (M), in particular a pinion (60), mounted free in rotation relative to the support but linked in translation to this support, this rotary member (M) being able to roll, without sliding, against the inner surface d '' a track (62), in a circular crown arc, fixed relative to the above-mentioned frame, a connecting rod (64, 64a) or   equivalent, being provided between an eccentric point (65) of the rotary member and a radial extension (66, 73) linked in rotation to the shaft (29) of the crank.   10. Device according to claim 9 characterized in that the support (59) is formed by at least one flat element (67, 68), or equivalent, linked in rotation to the hollow shaft (47) intended to control the head drive (5), this flat element, the mean plane of which is orthogonal to said shaft (47) extending radially and carrying, at its end remote from the shaft, the aforesaid rotary member (M, 60) 11. Device according to claim 10 characterized in that the support (59) is formed by two flat elements (67, 68) parallel, spaced from one another in the direction of the hollow shaft (47), each flat element carrying, inwards, a rotary member, advantageously a pinion (60), while the connecting rod (64, 64a) is located between the two pinions (60), each pinion cooperating with a circular crown provided inside a bolt bowl (63) fixed on the frame.